Diametrically cooperating vane pump



Jan. 31,, 1950 .J. R HIGHER 2,495,771

DIAMETRICALLY COOPERATING VANE PUMP Filed Oct. 15, 1945 2 Sheets-Sheet 2 Patented Jan. 31, 1950 UNITED STATES PATENT OFFICE ,Joseph 'R. Richer, Cleveland, -Ohio i-Ella IjRicher :administratrixf;Joseph-.R.- Richer, deceased "Application October 15, 1945; Serial'No. 622,433

'1 Claim.

The invention relates to rotary pumps and "more particularly to vane type pumps.

"Oneobject of the -invention is to provide a 'novel vane type pump :characterized particularlyby its high efficiency, freedomfrom wear, and the overall simplicity of its construction.

Another object is toprovide animproved .vane

type pump adapted to 'deliver a smooth, substantiallyuniform'flow of'fluid with a minimum of pulsations.

Another object is' to provide a vane type pump having novel-means for accurately locating the vanes withrespect atolthe walls of the pump W chamber so as to r minimize "slippage 'or internal leakage and: at the :same ktime-reduce the wear 'on the vanes and chamberwallsto'aminimum.

Another object is tot'provide airotor for avane pumps-embodying novel features of construc- 'tion which greatly ffaeilitate' the.;manufacture. .of the rotor and which. eiiectuallyiprevent distor- :tion of the same in: use.

Still another. object isito prof/idea flOtfilfyPlHIlI) constructed in a novel manner to facilitate adjustment "ofnthezrotor :bearings: to compensate for wear.

Other "objects: and advantages of the invention "Wi11':beC0meapparent from/the following zdetailed :description 1 of a the preferred embodiment illustrated in the accompanying drawings in which:

Figure 1 isian -end elevationaltviewiof the imzprove'd'pump'withione end rsectionrof the housiingremoved and with some parts broken away.

*Fig. 2iis-a longitudinal se'ctional view' of-the .pump" taken; in azverticali plane substantially :on the line 2-2 of Fig. 1.

Fig. 3'isa-perspective view of one of themtor vanes.

Fig. 4 is a diagrammatic view showing the. form of the-pump chamber.

Fig. -5 is a-diagrammatic' viewvsimilarto Fig. 4 but showing the irotor in'a 'different angular position.

"Referring'to Figs/71 and 2 "of the drawings,

:the pump selected to illustrate the invention comprises a housing r H] forming -a compart-k ment for an annular membervor barrel *ll defining a generally cylindrical; pumpchamben and a rotor'l2 carryinga plurality "of-radially projecting 'blades or vanes 13 adapted to cooperby bolts I4. Openings "ta-and *ffizatxopposite 2 sides of the body l5 may be'used'interchangeably as fluid'inletand outlet ports depending upon'the direction of rotation of the rotor l2.

'The rotorllcornprises a cylindrical body?!) provided at oppositeends with shaft extensions 2! and' 22 by which it is rotatablysupported'in en'd sectionsifi and l'l' of thei housing. In the exemplary pump, the shaft portion 21 iisformed integrally with the body 20 of the rotorand is extended through the end section is asat *2! 'to'provide for attachment of a drivinggearzor pulley. The shaft 22 is "preferably *removably securedto the body 'of the .rotorsas'by screws .23projecting through a flange 24-integraliwith the shaft.

As will be seen by reference to Fig. 2 of the drawings, the body 20 L of the -rotoriissulostan- 'tially longer "than the'barrel H 'formingfthe pump chamber and extends therethrough'to seat 'in recesses '25 and 26 in the endm-embers l6 and H. The end memberlfiisformedwitha :hub-like extension 21 axially'allned with'therecess 2125 and provided with -a..counterbore forming a seat fora roller bearing-28 .in' which the shaft 2! is journaled. A-nutizllthreaded.onzthe shaft and arranged to bear-against the :outer 'endof the bearing ,racering provides for ad- 'justment "of 'the shaft iaxially :of the bearing. Preferably, the bearing 28 isheldlinits seat :by a retaining ring andlawcap 3i removably. secured to the outer face'o'fthe endmember 18 as by machine. screws 32. Suitable glands or packing rings 33:. and 34 arranged onropposite :sides of the bearing prevent 3 leakage "of lubricant around the shaft.

'.In the particular .pum construction-illustrat- -ed,:the hub portion of theendrmember I'Biis formed with radially projecting ears 35 .for mounting the pump. on amachine frame: or :other suitable support. The ears-are apertured 'zasat 36'for the accommodation of'boltsby which the :pump is removably: attachedto. its support.

-Theendmember ll of the housing isgenerally similar to the companion endtmember, having 45 a hub portion '53! counterbore'dto ;provide a seat for a rollerbearing 38-uin*whichzthe shaft '22 is journaled. A flangedzretaining member 39 :secured to thecend ofithe shaft 22 as by a screw -40 retainstheshaft and bearing-in assembled relation. A cap il removably securedcto the end section I! 'protectsatherloearing'and, .insconiunction with'a gland or packingming 42,;serveszto retain the lubrieantiin the tbearingirecess.

'zInthe exemplarypump; the rotors tZ-isequipped with .a' pair of pthe vanes I 3 disposed :at :right angles to each other. The vanes may be alike and, as shown in Fig. 3, each consists of a flat, generally rectangular sheet metal plate formed with a central notch 45 of a depth equal to onehalf the width of the plate to permit them to be interfitted in crossed relation. In practice, the vanes are dimensioned crosswise so as to fit snugly between the end members It and ll of the pump while the lengthwise dimensions are such as to enable the vanes to coact with diametrically opposite walls of the pump chamber defined by the barrel l I.

To accommodate the rotor blades, the body 20 of the rotor is formed with transverse slots 46 opening in the end to which the shaft 22 is secured. The slots 46 are dimensioned to receive the vanes-with a sliding fit and are preferably of a slightly greater depth than the width of the vanes to permit adjustment of the pump body axially of the pump chamber to take up the wear on the rotor bearings.

By reason of the novel means provided for preventing warping, the rotor body may be hardened after the slots 46 are formed and thereafter ground to exact dimensions. For this purpose, the rotor body 20 is formed at one end with an axially projecting pad 4'! having a relatively shallow cylindrical recess 43 adapted to receive a cylindrical plug 49. After the slots 45 are cut on the rotor body, the plug 49 is inserted in the recess and acts to prevent the slotted end of the body from warping during the hardening process. The plug, of course, is removed for the insertion of the blades I3 and is reinserted in its recess after assembly of the blades with the rotor.

Distortion of the rotor during the operation of the pump is effectually prevented by forming the flange 24 of the shaft 22 with a recess 58 adapted to receive the pad 47 with a relatively snug fit. Thus when the rotor parts are assembled, the slotted sections of the rotor body are locked between the plug 49 and the walls of the recess 50 and effectually held against movement radially of the rotor body.

As indicated above, the working chamber of the pump is defined by the barrel H which is readily replaceable in case it becomes worn in use. Referring to Figs. 1 and 2 of the drawings,

the barrel II as herein shown comprises a generally cylindrical casting having radially projecting flanges and 52 at opposite sides. The flanges are dimensioned to provide a tight sliding fit in recesses 53 and 54 formed in the inner walls of the central section I5 of the housing midway between the ports l8 and IS. The flanges and the barrel II thus divide the interior of the housing into two separate compartments 55 and 56 associated respectively with the ports I9 and I8 and communicating with opposite sides of the pump chamber through ports 51 and 58 formed in the peripheral walls of the barrel. Set screws 59 threaded into the housing I5 and bearing against the flanges 5| and 52 provide means whereby the barrel may be adjusted transversely of the rotor axis to take up any wear which may occur on extended use.

As will be seen by reference to Fig. 1 of the drawings, the barrel H is mounted in the housing l0 so that the rotor I2 is disposed eccentrically therein. More specifically, the barrel is mounted So that the rotor is substantially in contact with the inner wall at the upper end of the barrel and spaced from the wall at the lower end of the barrel. This space forms a 4 channel 60 through which fluid is carried between the ports 51 and 58 by the vanes I3 as will appear presently.

The inner peripheral wall of the barrel II is shaped in a novel manner to enable the pump to deliver a smooth uniform fiow of fluid substantially without pulsations. As shown in Figs. 4 and 5, a section A of the wall in the upper part of the pump chamber is formed on a radius R substantially equal to the radius of the rotor and having its center C coaxial with the rotor. The section A extends through an arc of approximately degrees and corresponds to the spacing of adjacent vanes I 3.

Diametrically opposite the section A, the pump chamber walls are formed with a section B having a radius R1 having the same center C as the radius R but longer by an amount corresponding to the difference between the length of the vane l3 and the diameter of the rotor 12. Thus, the surfaces A and B are spaced apart substantially the length of a vane so that the opposite ends of the vane may coact therewith. The section B extends through an are slightly greater than 90 degrees, preferably by an amount substantially equal to the thickness of one of the vanes l3.

The wall sections A and B are joined by arcuate wall sections D and E containing the ports 5? and 53. These wall sections are formed on radii R2 and R3 of equal length but having their respective centers C1 and C2 located below and in lateral spaced relation to the center C of the rotor. It has been found that the accurate formation of the surfaces of the sections D and E is facilitated and maximum efliciency is obtained by locating the centers C1 and C2 on axes a: and 11 passing through the center C and disposed at angles of 45 degrees to a line a connecting the mid-points of the wall sections A and B. By reason of their circular form, the several wall surfaces of the pump chamber may be finished with a high degree of precision by simple grinding operations.

The particular shape and location of the wall sections D and E are also advantageous in shifting the vanes l 3 transversely of the rotor as they pass from the channel 60 of the pump chamber defined. by the rotor and the wall section B to the opposite wall section A. Wall section D performs that function when the rotor turns clockwise as viewed in Fig. 4 while wall section E shifts the vanes upon reverse rotation of the rotor. It will be evident that in the first instance, port 58 serves as the inlet and port 57 as the outlet, while in the second instance the functions of the ports are reversed. In either case, the shifting of the vane is timed so as to close the inlet end of the channel before the outlet end is opened by the passage of the companion vane from the wall section B. slippage or internal leakage between the inlet and outlet ports is thus avoided.

Leakage between the vanes and the wall section B is reduced to a minimum and wear on the vanes and on the chamber wall is reduced to a minimum by the novel arrangement provided for confining the radial projection of the vanes within accurately defined limits. For this purpose, the slots 45 in the vanes are formed with a width such that the ends of the vanes just clear the surface of the wall section B when the edge of the slot of one vane engages the side of the companion vane. Each vane therefore acts as a positive stop for the companion vane and accurately determines the limit position when projected radially from the rotor.

The operation of the improved pump will be readily apparent from the foregoing description. Assuming that the rotor is driven in a clockwise direction as viewed in Fig. 4, fluid is admitted through the inlet ports l9 and 58 at the right side of the pump to the inlet section of the pump chamber defined by the wall section E. As the projecting end of the vane moving along the wall section D approaches the section A, the vane is shifted across the rotor into close proximity to the right edge of the wall section B thus closing the inlet end of the channel 60.

While the foregoing is occurring, the companion vane is moving along the wall section B to force out the charge of fluid previously received as that vane passed the inlet port. The fluid entrapped between the two vanes is carried along the channel to be discharged at the outlet port when the leading vane passes from the wall section B. Thus the vanes act alternately to draw fluid through the inlet port and carry it through the channel 60 of the pump chamber to the outlet port. Leakage between the ports is effectually prevented since the inlet end of the channel 60 is closed before the outlet end is opened for the discharge of fluid. Moreover, as the leading vane passes from the wall section B to the wall section D, the chamber is opened gradually to the outlet port to permit a smooth, pulsationless discharge of fluid through the port.

The operation of the pump is substantially the same upon rotation of the rotor 12 in the opposite direction. Under such conditions, fluid is drawn in through the ports l8 and 51 and discharged through the ports l9 and 58. The wall of the pump structure. In general the improved pum is characterized by its simplicity of construction which greatly facilitates manufacture and assembly of the parts and which materially reduces its cost.

I claim as my invention:

In a pump, in combination, a barrel forming a pump chamber having inlet and outlet ports at opposite sides, said chamber having arcuate wall sections between said ports formed on a common center, one of said wall sections having a greater radius than the other section, a cylindrical rotor mounted in said chamber with its rotational axis coincident with the common center of said wall sections, said rotor having a pair of transverse slots disposed at right angles to each other and intersecting at the axis of the rotor, at vane mounted in each slot for endwise sliding movement across said rotor, said vanes having cooperating notches at their point of intersection of a depth equal to one half the width of the vane to allow the vanes to slide relative to each other, the widths of said notches being such that each vane is operative to block the other vane and maintain the end of the other vane in spaced relation to said one wall section during its passage thereover.

JOSEPH R. RICHER.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 353,199 Brewer Nov. 23, 1886 1,339,347 Jackson May 4, 1920 1,989,864 J aworowski Feb. 5, 1935 2,293,119 Davis Aug. 18, 1942 FOREIGN PATENTS Number Country Date 8,344 Germany June 22, 1879 11,435 Great Britain May 26, 1908 23,978 France Sent. 27, 1921 286,240 Great Britain Aug. 27, 1927 463,418 Great Britain Mar. 30, 1937 512,155 France Oct. 7, 1920 

